US5564510A - Pneumatic drill hammer - Google Patents

Pneumatic drill hammer Download PDF

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Publication number
US5564510A
US5564510A US08/356,003 US35600394A US5564510A US 5564510 A US5564510 A US 5564510A US 35600394 A US35600394 A US 35600394A US 5564510 A US5564510 A US 5564510A
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drill hammer
adapter
hammer according
drill
shaft
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Expired - Fee Related
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US08/356,003
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English (en)
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Hans-Philipp Walter
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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/06—Down-hole impacting means, e.g. hammers
    • E21B4/14—Fluid operated hammers

Definitions

  • the invention relates to a pneumatic drill hammer, in particular a downhole percussion hammer according to the generic portion of claim 1.
  • a downhole hammer comprises a central tube for guiding a ram above which is a sleeve valve with transverse passages for controlling the pressure conditions in the hammer as well as its blowout; such a design is comparatively expensive. It has also been proposed to have the ram slide in a case fixed inside an outer tube, but that may pose problems and is prone to technical trouble. Much the same holds for drill hammers as disclosed in DE-B-2 062 690 and in EP-A-0 484 672.
  • a drill hammer of the type initially mentioned is described in DE-U-9 202 336. Being well suited even for difficult mining work, this hammer includes a rotatory tubular body for proportioning the blowing air and further includes a shaft which has a central passage and is shiftable inside the tubular body. Together with the latter or with a sleeve component, the lower shaft end forms a shut-off device such as a rotary or parallel slide valve for opening or--possibly in part only--for closing an air deviating volume, as may be required.
  • a shut-off device such as a rotary or parallel slide valve for opening or--possibly in part only--for closing an air deviating volume, as may be required.
  • a neck of the shaft that is drivingly connected with the tubular body and a tube head having a plurality of peripheral bores may be fragile due to relatively weak cross sections, the more so since in operation, the full drill hammer length will be effective with a large lever arm.
  • the invention further aims at a hammer of high performance combined with a long service life.
  • Yet another objective consists in creating a hammer of such structure that it will operate smoothly and with low compressed air demand even at increased percussion frequencies.
  • a pneumatic drill hammer in particular a downhole percussion hammer, including of an upper end for connection to a compressed air supply and possibly to a drill string, of an outer tube, of a central tube which has radial passages, is arranged downstream of a check valve and is rigidly attached to a control casing jacket, and of a drill steel shiftably retained at the lower end of the outer tube, a head portion of the drill steel being adapted to slide onto a lower end of the central tube that thereabove guides a ram also guided in a cylinder liner, the invention as characterized in claim 1 provides for the cylinder liner and the control casing jacket to be at least in part positively fitted to the outer tube so as to form a rigid assembly therewith.
  • a lower end of the cylinder liner joins, with identical diameter, a shoulder in the outer tube and is concentrically fixed to the control casing jacket, e.g. by lodging the lower end of a tubular body, whereby the cylinder liner is firmly secured in a centered manner.
  • the tops of the outer tube and of the control casing jacket are trim flush and are peripherally welded without welding fillers, especially along an axial range (welding zone S, length l) with the ratio between the welding zone length and the outer diameter of the outer tube being in the range of 1:1.5 to 1:1.8.
  • Outer flutes as defined by claim 4 permit the application of screwing tools which, compared to the common clamping jaws, is quite advantageous for practical handling.
  • the design according to claims 5 to 8 comprises staggered outer ribs on portions of the cylinder liner for easing the air flow and, at the same time, securely bearing on the outer tube. If they extend parallel to a longitudinal hammer axis and are structured in uniform ring arrays in such manner that the peripheral distance between neighboring outer ribs amounts to a multiple of the rib width, there are wide free cross sections in the space towards the outer tube whereby the hammer operation is enhanced. Air distribution is further promoted by interstitially staggering axially subordinated ring arrays of outer ribs that engage the outer tube inside and, at the same time, allow for partial flow in a peripheral direction.
  • the ring arrays may be spaced by axial distances of the order of the rib length so that balancing interchambers are formed which contribute to an even air flow.
  • An important improvement for which independent protection is sought comprises, according to claim 9, directly joining the top of the control casing jacket to the screw head or to a lower portion of an adapter by a threading that extends parallel to the welding zone essentially along the latter's axial length or beyond it. Due to the safe fit, such an adapter permits using the drill hammer under most variegated conditions of operation with a maximum service life.
  • the adapter includes downstream channels that open out towards a ring strainer held by a filter ring which engages an adapter shoulder and, by claim 11, comprises uniformly spaced and upwardly extending peripheral openings such as bores, nozzles, etc. that open out obliquely or curvedly towards an upper outer region where the filter ring is tapered, preferably with a conically reentering portion.
  • Permanent stability of the drill hammer is further assisted according to the important feature of claim 12 that a rotatory sleeve is engaged between the adapter and the screw head, the outer diameter of the sleeve equalling that of the outer tube and the sleeve being drive-connected to the adapter either directly or via a shift unit guiding a shaft. Consequently, a very short shaft with two neighboring guide components will do for the power train.
  • the drive shaft is sleeve-protected at the decisive point immediately below the screw head.
  • the novel drill hammer is much more sturdy not only because of its comparative shortness but also since the blowing ring situated on the adpater is directly adjacent to the threaded sleeve.
  • a modification specified in claim 16 provides that the lower end of the shaft comprises a control slide valve having passages and annular areas for air control in combination with a collar in the upper portion of the adapter, a transition volume in the shift unit being flow-connected to downstream channels arranged substantially axially parallel in the upper portion of the adapter and at least some passages being flow-connected, in an upper position of the shaft, to the downstream channels.
  • An embodiment as defined by claim 17 includes in the adapter a valve seat for the check valve that is arranged at the control casing jacket and is, together with a valve spring pertaining thereto, supported by a base having channels which extend from a passage to a chamber of the control casing jacket.
  • This structure is both simple and sturdy.
  • the valve support by the base immediately adjacent the lower adapter portion has proved its merits. Continuing passages, channels, recesses, etc. serve for suitable air flow towards the drill hammer bottom.
  • the tubular body includes radial bores flow-connected via annular recesses with each other and with radial bores in the control casing jacket, the latter bores opening into a jacket chamber.
  • Air feeding for charging the ram is controlled by the number, size, and arrangement of these radial bores and of the recesses associated thereto.
  • the jacket chamber which is situated between the outer tube and the cylinder liner and which has a free cross section at least as wide as the most narrow one of the central passages in the main components of drill hammer (claim 19). Such dimensioning will safeguard good air flow against flow resistance that is at least substantially uniform.
  • FIGS. 1a-1b are a longitudinal section through a drill hammer in its blowout position
  • FIGS. 2a-2b are a divided longitudinal section through a drill hammer in two different operational positions
  • FIG. 3 is a longitudinal section through the upper portion of a drillhammer of simplified design
  • FIG. 4 is a longitudinal section through the upper portion of another drill hammer embodiment in two operational positions
  • FIGS. 5a to 5d are lateral and sectional views, respectively, of blowing collar components and its assembly
  • FIG. 6 is a longitudinal section through a central and lower portion of yet another drill hammer embodiment
  • FIG. 7 is an axial section and lateral view of a cylinder liner
  • FIGS. 8a to 8c are partial longitudinal sectional views of further variants with different ram positions.
  • FIG. 1a and FIG. 1b are meant to be joined and together form FIG. 1; likewise, FIG. 2a and FIG. 2b should be joined to commonly form FIG. 2.
  • They show a drill hammer 10 having a screw head 11 and a central passage 12, a threading 13 followed by a seal ring 14 and a tapped sleeve 16 within a sleeve 15 that guides a shaft 20.
  • a shaft head 19 is screwed to the tapped sleeve 16;
  • a central passage 17 is hexagonally shaped for receiving a screwing tool (not shown).
  • the shaft 20 is provided with a spline-type rib profile 21 that positively fits a matching counter-rib profile 31 in an upper portion of a shift unit 30.
  • a central passage 22 leads down to a lower end 23 of the shaft 20 where there is a shoulder 26 and, inside, a lead-in opening 27.
  • a slideway 25 at a lower end 24 of sleeve 15 guides a neck 35 of shift unit 30.
  • the latter as well as sleeve 15 and screw head 11 are provided with outer flutes R for receiving a screwing tool (not shown).
  • the lower end 24 of sleeve 15 is opposite a shoulder 34 of shift unit 30 which comprises, in addition, an inner stop 36 opposite to the shoulder 26 of shaft 20.
  • a transition volume 32 joining an upper portion 41 of an adapter 40 so that a flow connection is provided to a central passage 42 therein and to outer downstream channels 43.
  • the upper portion 41 includes an upwardly extending neck 44.
  • a blowing collar 50 whose structure is seen from FIGS. 5a to 5d is located at a shoulder 46.
  • sleeve 15 encompasses an annular space where an annular manifold 103 (FIG. 3) may be situated that has passages 104 for continuous blowing operation.
  • adapter 40 In a central portion of adapter 40, its passage 42 widens conically for transition to a chamber 47 whose top is designed as a valve seat 49. While there is a threading 38 for screwing the upper portion 41 to the shift unit 30, another threading 48 at the lower portion 45 serves for connection to to an outer tube 55 which--like the adapter 40--is provided with outer flutes R.
  • outer tube 55 is welded to a control casing jacket 60 in a welding zone S of an axial length l that roughly corresponds to the length of threading 38.
  • the lower portion 45 of adapter 40 abuts on a base 54 which is a support for a check valve 59 with valve spring 58 and which includes channels 63 opening out to a chamber 62 of a central tube 80.
  • the control casing jacket 60 has radial bores 64 that may be offset relative to each other in axial and peripheral directions. They open out in an annular recess 65 that is flow-connected via radial bores 67 to a jacket chamber 68 situated between a cylinder liner 70 and the unit of outer tube 55 and control casing jacket 60 welded at its upper end.
  • Jacket chamber 68 terminates at a step 57 of outer tube 55 and comprises upper radial bores 71 as well as central radial bores 72 that function as an inlet port.
  • central tube 80 Inside conctrol casing jacket 60, there is a tubular body 61 continued by the central tube 80 which has transverse bores 81 in an upper region and radial bores 83 in a lower region. Immediately above lower end 84 of central tube 80, it is provided with a recessed portion 107 of smaller outer diameter (see FIGS. 8a, 8b, 8c), but a uniform central tube 80 is also possible (FIGS. 1b, 2b). In either case, tube 80 guides a ram 75 that is also guided in the cylinder liner 70, has annular recesses 76, 76' and comprises axial bores 78, 78'. A top face 74 of ram 75 is opposite a bottom face 69 of tubular body 61; a bottom face 79 of ram 75 is to hit periodically on an opposite impact face 89 of a drill steel 90.
  • Drill steel 90 includes a shaft 87 having a shoulder 88 held by a support ring 86.
  • a bumper sleeve 85 guides shaft 87 at an upper portion thereof.
  • a passage 92 is shaped as a lead-in bore 91 towards impact face 89 and coacts with the central tube 80 for air control, the lower end 84 being recessed (as described) for the purpose.
  • Drill steel 90 further comprises a support unit 93 having outer flutes R. In conventional fashion, the foot portion of drill steel 90 is provided with passages and pins or carbide tips (not designated).
  • FIG. 1 The lower portion of drill hammer 10 is seen in FIG. 1 in its elevated blowout position, i.e. clear of the ground in borehole B with the drill steel 90 being suspended.
  • shoulder 26 of lower shaft end 23 engages stop 36 of shift unit 30 so that neck 44 of adapter 40 is free.
  • Air fed through central bores 12, 22 of screw head 11 and shaft 20, respectively, is branched to that a partial flow goes through passage 42 of adapter 40 and presses on check valve 59 moving it into an open position (FIG. 1); the remaining air flow passes through the downstream channels 43 of adapter 40 and through ring strainer 51 as well as nozzles or slanted bores 53 of blowing collar 50.
  • the turn of the air flow generates a Venturi effect causing suction in the way of a jet blast pump so that the drillings are drawn up from the borehole bottom and blown out.
  • the partial or branched flow quantities can be proportioned as required by selecting the number and size of the passages, channels, bores, etc.
  • drill hammer 10 In its blowout position (FIG. 1), drill hammer 10 is lifted off the ground whereby drill steel 90 is supported under upstream air and its shoulder 88 is suspended on supporting ring 86 while bumper sleeve 85 is engaged by ram 75 whose top face 74, therefore, is below the radial bores 71 of cylinder liner 70.
  • compressed air flows through channels 63 into chamber 62 of central tube 80 and via bores 64/65/67 into jacket chamber 68, along outer tube 55 towards the radial bores 71 and into axial bores 78 but also through transverse bores 81 and central bore 82 in shaft 87 of drill steel 90 so as to blast the borehole bottom.
  • lower shaft end 23 in the upper portion of drill hammer 10 encompasses neck 44 of adapter 40, and shoulder 26 shuts off the downstream channels 43.
  • Compressed air fed will pass through all the central bores and passages 12, 22, 42/47, 62, 82, 92 of the main hammer components 11, 20, 20, 40, 61, 80, 87/90 so that drill steel 90 hammers onto the borehole ground.
  • partial flow quantities may be branched towards blowing collar 50 by suitably dimensioning or adjusting an annular gap between neck 44 of adapter 40 and shoulder 26 of shaft 20 so as to obtain a slide valve action.
  • FIG. 3 represents the upper portion of a drill hammer embodiment that is simplified by omitting shaft 20 and shift unit 30.
  • Sleeve 15 attached to screw head 11 is directly screwed to adapter 40 via threading 38.
  • Compressed air is fed through annular manifold 103 and its passages 104 through the passages 12, 42 towards the lower hammer portion (not shown here). Again, blowout is effected through the downstream channels 43 and the bores 53 of blowing collar 50, with the ratio of branched air quantities being determined by the number and dimensions of the passages, channels, bores, etc.
  • lower end 23 of shaft 20 acts as a slide valve vis-a-vis e.g. two annular areas 29, 29' and a number of neighboring passages 28, 28', 28".
  • the upper annular area 29' will shut off the top of passage 42 in adapter 40 so that the total air flow will pass into the lower hammer portion screwed on (not shown here) through the passages 12, 22, 28'/28, 42 of the components 11, 20/23, 40.
  • the slide valve design of FIG. 4 will, in combination with the embodiments shown in FIGS. 8b and 8b, ensure continuous operation in a surprisingly simple mode with exactly metered partial air quantities.
  • ram 75 will continually oscillate even when the drill hammer 10 is lifted, producing jolts and vibrations that are desirable for some rock formations and else may be essential, such as with overburden, salvage, cleavage, fissures, etc.
  • the ram stroke as well as the impact energy may be sufficiently reduced in order to avoid excessive stress on the drill hammer 10 so that its self-destruction is definitely prevented.
  • the air flow fed through passage 22 will be branched so that downstream air will partly exhaust to ambience through the passages 28', 43, 53 while a partial quantity will flow down into the lower hammer portion through the bottom passage 28 and a narrow annular space present between ring area 29 and collar 37.
  • branching ratios may be arranged for as required by suitably dimensioning the passages, channels, bores, etc.
  • FIG. 6 Another version of the drill hammer 10 featuring valve control and adjustable upstream air is shown in FIG. 6 where like components are identified by the same reference symbols as hereinabove.
  • the design again comprises a central tube 80 but includes a cylinder liner 70 having outer ribs 101 and a control valve 97 in a control casing jacket 60 axially welded to the outer tube 55. If the hammer 10 is lifted off the borehole ground, the bottom face 79 of ram 75 will engage the bumper sleeve 85.
  • FIG. 6 displays a flapper-type control valve 97 in a neutral position; other valves, however, can also be employed.
  • a flap is borne on a central support, e.g. a prism 98, on top of control casing 96. If the flap tilts (to the right in FIG. 6), a lefthand passage (not shown) will open and air can flow through bores (not shown) in control casing 96 into chamber 62 of central tube 80 and, via bores 99, into the space between top face 74 of ram 75 and bottom face 69 of control casing jacket 60. As the ram 75 goes down, the pressure above it will decrease when its top face 74 passes the upper edge of the transverse outlet bores 81 in central tube 80.
  • novel drill hammer 10 provides control via the central tube 80 irrespective of the axial extension of ram 75. This results in high impact frequency on account of the full upstream air pressure acting on the large bottom face 79, and in fast upward acceleration.
  • conventional drill hammers having a ram either without bore or, if with bore, without a central tube have only a relatively limited space for upstream air and are designed for high energy of each impact so that the hammering frequency is rather low.
  • a modified embodiment (not shown) comprises a solid ram without outer axial bores, annular grooves, etc. but with the inlet port 72 being so low that upstream air flowing when the drill steel 90 touches ground will lift the ram 75 from below.
  • FIGS. 8a to 8c Further drill hammer versions are seen in FIGS. 8a to 8c where the ram 75 guided on central tube 80 goes down into bumper sleeve 85. No matter how long the ram 75 is, upstream air will be governed by the radial bores 83 in central tube 80. (By contrast, conventional hammers without a central tube require a ram of great length in order to collect a sufficient quantity of upstream air during its stroke.)
  • FIG. 7 shows a special cylinder liner 70 having a plurality of outer ribs 101 arranged at peripheral distances w in staggered ring arrays 102 of such axial distances p that both great throughflow volume and good support at the inner wall of outer tube 55 are attained.
  • the individual ring arrays 102 are interstitially located so that neighboring arrays 102 will be peripherally displaced by, say, half the peripheral rib distance w which is a multiple of rib width n, in particular two to five times as large.
  • the axial distances p may roughly correspond to rib length m but may alternatively be shorter so that the ring arrays 102 will be closer to each other.
  • FIG. 8a shows the central portion of a drill hammer 10 for intermittent operation.
  • ram 75 contacts bumper sleeve 85, shutting off the upstream inlet port 72 but relieving upper blowout bores 106 whereby the hammer operation may be stopped.
  • FIGS. 8b and 8c are analogous to FIGS. 4 and 6, showing the central portion of a drill hammer 10 designed for continuous operation.
  • the drill steel 90 is yet in its suspended position with the extended wider end 84 of central tube 80 shutting off the lead-in bore 91 of shaft 87, whereby the upper hammer portion (FIG. 4) will supply a reduced quantity of air.
  • the down-going ram 75 will self-produce buffering in the closed volume 94 so that contact between ram 75 and bumper sleeve 85 as well as drill steel 90 will be prevented.
  • the upstream air pressure will move the ram 75 upwards then (FIG. 8c) and as soon as it shuts off the outlet bores 81 in buffer volume 95, ram 75 will start oscillating.
  • the drill hammer 10 generally comprises an outer tube 55, a control casing jacket 60 inclusive of check valve 59 and a central tube 80 having radial passages 81,83.
  • a ram 75 is guided on central tube 80, onto the lower and preferably recessed end 84 of which the head of a drill steel 90 may slide.
  • a cylinder liner 70 that may be provided with outer ribs 101 also guides ram 75 and is peripherally welded to outer tube 55 along a welding zone S of axial length l.
  • Above control casing jacket 60 there is an adapter 40 comprising downstream channels 43 and carrying a blowing collar 50 provided with upwardly directed nozzles 53.
  • a drive-transmitting sleeve 15 below a screw head 11 is joined to adapter 40 either directly or via a shift unit 30 that guides a shaft 20 whose lower end 23 may form a slide valve relative to the upper adapter portion 41.
  • passages 42, 47 lead to a control casing jacket 62 having channels 63.
  • Below a tubular body 61 there is between outer tube 55 and cylinder liner 70 a jacket chamber 68 of a free cross section at least as large as that of the narrowest among the central passages 12, 22, 32, 42/47, 62, 82, 92 in the main components 11, 20, 30, 40, 61, 80, 87/90, respectively.
  • Grooves, channels and bores 71, 72; 81, 83 in cylinder liner 70 and central tube 80 serve, together with recesses 76, 76' and bores 78, 78' for controlling the movement of ram 75.

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  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)
  • Drilling Tools (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
US08/356,003 1993-12-15 1994-12-14 Pneumatic drill hammer Expired - Fee Related US5564510A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9319223U 1993-12-15
DE9319223U DE9319223U1 (de) 1993-12-15 1993-12-15 Bohrhammer

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US (1) US5564510A (fr)
EP (1) EP0658681B1 (fr)
AT (1) ATE191055T1 (fr)
AU (1) AU677874B2 (fr)
CA (1) CA2138086A1 (fr)
CZ (1) CZ285685B6 (fr)
DE (2) DE9319223U1 (fr)
ES (1) ES2147212T3 (fr)
ZA (1) ZA949802B (fr)

Cited By (13)

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Publication number Priority date Publication date Assignee Title
US5680904A (en) * 1995-11-30 1997-10-28 Patterson; William N. In-the-hole percussion rock drill
US5937956A (en) * 1995-12-08 1999-08-17 Tracto-Technik Paul Schmidt Spezialmaschinen Ram boring machine
US6290002B1 (en) 1999-02-03 2001-09-18 Halliburton Energy Services, Inc. Pneumatic hammer drilling assembly for use in directional drilling
US6499544B1 (en) * 2000-11-15 2002-12-31 Sandvik Ab Percussive down-the-hole hammer for rock drilling, and a one-way valve used therein
US6883618B1 (en) * 2004-06-15 2005-04-26 Numa Tool Company Variable timing for front chamber of pneumatic hammer
US20050241842A1 (en) * 2004-04-29 2005-11-03 Brent Marsh Reciprocable impact hammer
US20070251710A1 (en) * 2004-12-07 2007-11-01 Byung-Duk Lim Ground Drilling Hammer and the Driving Method
US20100300763A1 (en) * 2006-10-20 2010-12-02 Drillroc Pneumatic Pty Ltd Down-the-Hole Hammer Drill
US9016404B2 (en) 2009-08-24 2015-04-28 Tracto-Technik Gmbh & Co. Kg Ram boring device
US9068399B2 (en) 2006-10-20 2015-06-30 Drillroc Pneumatic Pty Ltd Down-the-hole hammer drill
WO2020148333A1 (fr) * 2019-01-15 2020-07-23 Pml Energy Ab Système de forage de roche pour forage géothermique, procédé et utilisation d'un tel système de forage de roche
EP3725997A4 (fr) * 2017-12-13 2021-07-28 Jaime Andres Aros Système d'écoulement de fluide sous pression comprenant plusieurs chambres de travail pour un marteau de fond de trou et marteau de fond de trou à circulation normale comprenant ledit système
US11273546B2 (en) * 2019-01-25 2022-03-15 Jian-Shiou Liaw Valve seat of a pneumatic hammer

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29618066U1 (de) * 1996-10-18 1996-12-19 Walter, Hans-Philipp, 74251 Lehrensteinsfeld Bohrhammer
DE19804078A1 (de) * 1998-02-03 1999-08-05 Krupp Berco Bautechnik Gmbh Fluidbetriebenes Schlagwerk
DE102005015886B4 (de) * 2005-04-06 2008-06-19 Hans-Philipp Walter Bohrhammer
CN104278948B (zh) * 2014-09-28 2016-07-06 扬州天业石油机械有限公司 一种螺杆钻具传动轴总成
CN107829689B (zh) * 2017-11-21 2023-10-31 中南大学 多向喷射气动潜孔锤钻头

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EP0484672A1 (fr) * 1990-11-09 1992-05-13 PERMON, státni podnik Unité de forage pneumatique submersible
US5207283A (en) * 1992-03-02 1993-05-04 Ingersoll-Rand Company Reversible bit bearing
US5305837A (en) * 1992-07-17 1994-04-26 Smith International, Inc. Air percussion drilling assembly for directional drilling applications
US5318140A (en) * 1991-12-20 1994-06-07 Uniroc Ab Fluid operated drill apparatus

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US3225841A (en) * 1962-08-31 1965-12-28 Joy Mfg Co Drilling apparatus
GB1419981A (en) * 1973-01-09 1976-01-07 Halifax Tool Co Ltd Percussion drills
US3964551A (en) * 1974-09-20 1976-06-22 Reed Tool Company Pneumatic impact drilling tool
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DE8403508U1 (de) * 1984-02-07 1984-05-03 Walter, Hans-Philipp, 7102 Weinsberg Bohrhammer
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Publication number Priority date Publication date Assignee Title
US2996131A (en) * 1957-06-03 1961-08-15 Eugene C Greenwood Lubricant packed bumper sub
US3570611A (en) * 1968-02-09 1971-03-16 Trustul Deforaj Pitesti Device for freeing seized drill strings
DE2062690A1 (fr) * 1970-01-07 1972-03-09
DE2705191A1 (de) * 1976-02-09 1977-08-11 Reed Tool Co Schlagbohrwerkzeug
US4084647A (en) * 1976-07-01 1978-04-18 William Lister Pneumatic percussion hammer
US4312412A (en) * 1979-08-06 1982-01-26 Dresser Industries, Inc. Fluid operated rock drill hammer
US5107944A (en) * 1987-07-14 1992-04-28 Per Gustafsson Down hole drills using spent driving fluid for flushing purposes
US4878550A (en) * 1988-07-15 1989-11-07 Sandvik Rock Tools, Inc. Pilot-valve-controlled percussion drilling tool
EP0484672A1 (fr) * 1990-11-09 1992-05-13 PERMON, státni podnik Unité de forage pneumatique submersible
US5318140A (en) * 1991-12-20 1994-06-07 Uniroc Ab Fluid operated drill apparatus
DE9202336U1 (de) * 1992-02-22 1992-05-07 Walter, Hans-Philipp, 7102 Lehrensteinsfeld Bohrhammer-Gerät
US5207283A (en) * 1992-03-02 1993-05-04 Ingersoll-Rand Company Reversible bit bearing
US5305837A (en) * 1992-07-17 1994-04-26 Smith International, Inc. Air percussion drilling assembly for directional drilling applications

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US11273546B2 (en) * 2019-01-25 2022-03-15 Jian-Shiou Liaw Valve seat of a pneumatic hammer

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Publication number Publication date
ATE191055T1 (de) 2000-04-15
DE59409229D1 (de) 2000-04-27
CZ316194A3 (en) 1995-07-12
EP0658681A3 (fr) 1997-01-02
CZ285685B6 (cs) 1999-10-13
AU8046794A (en) 1995-06-22
DE9319223U1 (de) 1994-02-24
CA2138086A1 (fr) 1995-06-16
ZA949802B (en) 1995-10-02
EP0658681B1 (fr) 2000-03-22
ES2147212T3 (es) 2000-09-01
AU677874B2 (en) 1997-05-08
EP0658681A2 (fr) 1995-06-21

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